U.S. patent number 5,695,123 [Application Number 08/543,589] was granted by the patent office on 1997-12-09 for rotary sprinkler with arc adjustment device.
This patent grant is currently assigned to James Hardie Irrigation, Inc.. Invention is credited to Tuan Van Le.
United States Patent |
5,695,123 |
Le |
December 9, 1997 |
Rotary sprinkler with arc adjustment device
Abstract
A rotary sprinkler comprising a supporting structure and a
sprinkler head mounted for rotational movement on the supporting
structure. The sprinkler includes an arc controller for controlling
the magnitude of the arc through which the sprinkler head can
rotate and an arc adjuster for adjusting the arc controller to
thereby adjust the arc through which the sprinkler head can rotate.
The arc adjuster includes an arc adjust member mounted for rotation
with the sprinkler head and drivingly coupled to the arc controller
to adjust the arc through which the sprinkler head can rotate and
an arc adjust driver for rotating the arc adjust member. The arc
adjust member includes a plurality of seals integral with the arc
adjust member and a pointer for providing an indication of one end
of the arc through which the sprinkler head can rotate. The
supporting structure has a marker for providing an indication of
the other end of the arc through which the sprinkler head can
rotate, and the sprinkler head has indicia for use with the pointer
for indicating the magnitude of the arc through which the sprinkler
head can rotate.
Inventors: |
Le; Tuan Van (Diamond Bar,
CA) |
Assignee: |
James Hardie Irrigation, Inc.
(Laguna Niguel, CA)
|
Family
ID: |
24168665 |
Appl.
No.: |
08/543,589 |
Filed: |
October 16, 1995 |
Current U.S.
Class: |
239/259; 239/240;
239/242 |
Current CPC
Class: |
B05B
15/74 (20180201); B05B 3/16 (20130101); B05B
3/0431 (20130101) |
Current International
Class: |
B05B
15/00 (20060101); B05B 15/10 (20060101); B05B
3/02 (20060101); B05B 3/04 (20060101); B05B
003/16 () |
Field of
Search: |
;239/236,237,240,242,251,255,259,261,263,263.3 |
References Cited
[Referenced By]
U.S. Patent Documents
Other References
Chironis, Nicholas P., "Mechanisms & Mechanical Devices
Sourcebook", copyright 1991, p. 86..
|
Primary Examiner: Grant; William
Assistant Examiner: Ganey; Steven J.
Attorney, Agent or Firm: Myers; Richard L.
Claims
I claim:
1. A rotary sprinkler comprising:
a supporting structure having an inlet for receiving irrigation
water;
a sprinkler head mounted for rotational movement on the supporting
structure and adapted to receive irrigation water from the
inlet;
a drive motor carried by the supporting structure;
a drive train drivingly coupled to the motor and to the sprinkler
head to impart rotational movement to the sprinkler head;
an arc controller for controlling the magnitude of the arc through
which the sprinkler head can rotate;
an arc adjuster for adjusting the arc controller to thereby adjust
the arc through which the sprinkler head can rotate;
said arc adjuster including an arc adjust member mounted for
rotation with the sprinkler head and drivingly coupled to the arc
controller to adjust the arc through which the sprinkler head can
rotate;
an arc adjust driver accessible from outside the sprinkler
head;
the arc adjust member including a gear section drivable by the arc
adjust driver; and
said arc adjust member including a dynamic seal which rotates with
the sprinkler head and engages the supporting structure.
2. A rotary sprinkler as defined in claim 1 wherein the drive train
includes a rotatable drive shaft which extends from the supporting
structure to the sprinkler head and is drivingly coupled to the
sprinkler head to rotate the sprinkler head, a portion of said
supporting structure circumscribing the drive shaft adjacent the
sprinkler head and said dynamic seal seals against said portion of
the supporting structure.
3. A rotary sprinkler as defined in claim 1 wherein the arc adjust
member includes a pointer, the supporting structure has a marker
and said pointer and said marker provide a visual indication of the
opposite ends of the arc through which the sprinkler head can
rotate.
4. A rotary sprinkler as defined in claim 3 wherein the sprinkler
head has indicia for use with the pointer for indicating the
magnitude of the arc through which the sprinkler head can
rotate.
5. A rotary sprinkler comprising:
a supporting structure having an inlet for receiving irrigation
water;
a sprinkler head mounted for rotational movement on the supporting
structure and adapted to receive irrigation water from the
inlet;
a drive motor carried by the supporting structure;
a drive train drivingly coupled to the motor and to the sprinkler
head to impart rotational movement to the sprinkler head;
an arc controller for controlling the magnitude of the arc through
which the sprinkler head can rotate;
an arc adjuster for adjusting the arc controller to thereby adjust
the arc through which the sprinkler head can rotate;
said arc adjuster including an arc adjust member mounted for
rotation with the sprinkler head and drivingly coupled to the arc
controller to adjust the arc through which the sprinkler head can
rotate;
an arc adjust driver accessible from outside the sprinkler
head;
the arc adjust member being a one piece member and being drivable
by the arc adjust driver; and
said arc adjust member including a dynamic seal which rotates with
the sprinkler head and engages the supporting structure and a
static seal which engages the sprinkler head.
6. A rotary sprinkler comprising:
a supporting structure having an inlet for receiving irrigation
water;
a sprinkler head mounted for rotational movement on the supporting
structure and adapted to receive irrigation water from the
inlet;
a drive motor carried by the supporting structure;
a drive train drivingly coupled to the motor and to the sprinkler
head to impart rotational movement to the sprinkler head;
a reversing device for reversing the direction of rotation of the
sprinkler head;
an arc controller for controlling the magnitude of the arc through
which the sprinkler head can rotate;
an arc adjuster for adjusting the arc controller to thereby adjust
the arc through which the sprinkler head can rotate;
said arc adjuster including an arc adjust member mounted for
rotation with the sprinkler head and drivingly coupled to the arc
controller to adjust the are through which the sprinkler head can
rotate and an arc adjust driver for rotating the arc adjust member;
and
said arc adjustment member including a first seal integral with the
arc adjustment member for sealing a surface of at least one of the
sprinkler head and the supporting structure, the first seal having
dynamic characteristics for rotating with the sprinkler head and
engaging the supporting structure.
7. A rotary sprinkler comprising:
a supporting structure having an inlet for receiving irrigation
water;
a sprinkler head mounted for rotational movement on the supporting
structure and adapted to receive irrigation water from the
inlet;
a drive motor carded by the supporting structure;
a drive train drivingly coupled to the motor and to the sprinkler
head to impart rotational movement to the sprinkler head;
a reversing device for reversing the direction of rotation of the
sprinkler head;
an arc controller for controlling the magnitude of the are through
which the sprinkler head can rotate;
an arc adjuster for adjusting the arc controller to thereby adjust
the arc through which the sprinkler head can rotate;
said arc adjuster including an arc adjust member mounted for
rotation with the sprinkler head and drivingly coupled to the are
controller to adjust the arc through which the sprinkler head can
rotate and an arc adjust driver for rotating the arc adjust member;
and
said arc adjustment member including a first seal integral with the
arc adjustment member for sealing a surface of at least one of the
sprinkler head and the supporting structure; and
the sprinkler head having an inner wall and the arc adjust member
including an annular wall having external gear teeth driveable by
the arc adjust member and an internal surface providing said first
seal and sealingly receiving said inner wall of the sprinkler
head.
8. A rotary sprinkler comprising:
a supporting structure having an inlet for receiving irrigation
water;
a sprinkler head mounted for rotational movement on the supporting
structure and adapted to receive irrigation water from the
inlet;
a drive motor carried by the supporting structure;
a drive train drivingly coupled to the motor and to the sprinkler
head to impart rotational movement to the sprinkler head;
a reversing device for reversing the direction of rotation of the
sprinkler head;
an arc controller for controlling the magnitude of the are through
which the sprinkler head can rotate;
an arc adjuster for adjusting the arc controller to thereby adjust
the arc through which the sprinkler head can rotate;
said arc adjuster including an arc adjust member mounted for
rotation with the sprinkler head and drivingly coupled to the are
controller to adjust the arc through which the sprinkler head can
rotate and an arc adjust driver for rotating the are adjust member;
and
said arc adjustment member including a first seal integral with the
arc adjustment member for sealing a surface of at least one of the
sprinkler head and the supporting structure, the arc adjust member
having a wall which terminates radially outwardly in said first
seal, said first seal engaging the sprinkler head, said are adjust
member rotating with the sprinkler head and including an annular
dynamic seal depending from the wall of the arc adjust member and
engagable with the supporting structure.
Description
BACKGROUND OF THE INVENTION
A rotary sprinkler typically includes a sprinkler head mounted for
rotational movement on suitable supporting structure, a drive motor
driven by the irrigation water, and a drive train having a
rotational output and drivingly coupled to the motor and to the
sprinkler head so that the rotational output can impart rotational
movement to the sprinkler head. The sprinkler head rotates through
a desired arc in both clockwise and counterclockwise directions,
and the rotary sprinkler may also include a suitable mechanism for
causing periodic pauses in the rotation of the sprinkler head such
that the sprinkler head rotates intermittently.
A rotary sprinkler typically has a feature which permits adjustment
of the magnitude of the arc through which the sprinkler head
rotates. However, many rotary sprinklers do not provide any easy
way to identify the ends of the arc through which the sprinkler
head is set to rotate, and this can complicate installation of the
sprinkler. In addition, some rotary sprinklers do not provide any
way to read the magnitude of the arc directly. The rotary
sprinklers of which I am aware that do embody a feature enabling a
direct readout of the magnitude of the arc are more complex,
expensive and/or less reliable than desirable. These rotary
sprinklers employ a separate O-ring seal to seal out grit from this
region of the sprinkler.
SUMMARY OF THE INVENTION
This invention provides a rotary sprinkler which generally
overcomes these disadvantages. The rotary sprinkler of this
invention provides a visible indication of the ends of the arc
through which the sprinkler head is set to rotate and a convenient
readout of the magnitude of such arc. Moreover, effective sealing
against grit is obtained, and all of these features are provided in
a relatively inexpensive and uncomplicated manner.
This invention is adapted for use with a rotary sprinkler of a type
which comprises a supporting structure having an inlet for
receiving irrigation water, a sprinkler head mounted for rotational
movement on the supporting structure and adapted to receive
irrigation water from the inlet, a drive motor carried by the
supporting structure, a drive train drivingly coupled to the motor
and to the sprinkler head to impart rotational movement to the
sprinkler head, and a reversing device for reversing the direction
of rotation of the sprinkler head. The rotary sprinkler may also
include an arc controller for controlling the magnitude of the arc
through which the sprinkler head can rotate and an arc adjuster for
adjusting the arc controller to thereby adjust the arc through the
sprinkler head can rotate. The arc adjuster includes an arc adjust
member mounted for rotation with the sprinkler head and drivingly
coupled to the arc controller to adjust the arc through which the
sprinkler head can rotate and an arc adjust driver for rotating the
arc adjust member.
The arc adjust member provides many important features which can be
used individually or in combination. For example, the arc adjust
member, in addition to being a part of the arc adjuster, may
provide one or more seals which keep grit out of relatively moving
surfaces of the sprinkler. The arc adjust member may include a
first seal integral with the arc adjust member for sealing a
surface of at least one of the sprinkler head and the supporting
structure. This integral seal may eliminate the need for employing
a separate seal, such as an O-ring. The first seal may be a static
seal which engages the sprinkler head or the first seal may rotate
with the sprinkler head and engage the supporting structure whereby
the first seal is a dynamic seal. In a preferred construction, the
arc adjust member includes a plurality of seals including a dynamic
seal and one or more static seals which cooperate with the
sprinkler head.
Another feature of the invention is that the arc adjust member may
include a pointer for providing an indication of one end of the arc
through which the sprinkler head can rotate. The pointer is visible
from outside of the sprinkler such that the indication provided by
the pointer is visual.
The supporting structure may have a marker visible from the outside
of the sprinkler for providing a visual indication of the other end
of the arc through which the sprinkler head can rotate. To provide
a readout as to the magnitude of the arc, the sprinkler head
preferably has indicia for use with the pointer for indicating the
magnitude of the arc through which the sprinkler head can rotate.
In order that the pointer can properly cooperate with such indicia
on the sprinkler head, the arc adjust member including the pointer
are rotatable by the arc adjust driver relative to the sprinkler
head to set the arc through which the sprinkler head can rotate.
During this time of rotation, the seals referred to as static seals
are moving relative to the surface against which they are sealing.
However, they are considered static seals because during operation
of the sprinkler, as opposed to mere arc adjustment of the
sprinkler, there is essentially no relative movement between the
static seal and the sprinkler head.
The pointer can provide a visual indication of an end of the arc
through which the sprinkler head is set to rotate in various
different ways. Preferably, however, the pointer is visible between
the sprinkler head and the supporting structure.
Although the arc adjust member can be drivable by the arc adjust
driver in different ways, preferably the arc adjust member includes
a gear section which is directly driven by the arc adjust driver.
This enables the arc adjust member to be driven in rotation
relative to the sprinkler head to set the arc through which the
sprinkler head is to rotate.
In a preferred construction, the sprinkler head has an inner wall
and the arc adjust member includes an annular wall having external
gear teeth drivable by the arc adjust driver and an internal
surface sealingly receiving the inner wall of the sprinkler head.
The seal thus provided is a grit seal but this does not prevent
rotation of the arc adjust member relative to the sprinkler head to
adjust the arc of rotation of the sprinkler head. Preferably the
arc adjust member has a wall or flange which terminates radially
outwardly in a static seal which cooperates with the sprinkler
head. The arc adjust member rotates with the sprinkler head during
operation of the sprinkler and includes an annular dynamic seal
depending from the transverse wall and engageable with the
supporting structure.
In a preferred construction the drive train includes a rotatable
drive shaft which extends from the supporting structure to the
sprinkler head and is drivingly coupled to the sprinkler head to
rotate the sprinkler head. A portion of the supporting structure
circumscribes the drive shaft adjacent the sprinkler head. The
dynamic seal seals against such portion of the supporting
structure.
To further simplify construction, the arc adjust member is
preferably a one piece member. Thus, in a preferred construction a
single one piece member can provide both static and dynamic
sealing, a gear section that enables the setting of the arc and a
pointer which visually identifies one end of the arc.
The invention, together with additional features and advantages
thereof may best be understood by reference to the following
description taken in connection with the accompanying illustrative
drawing.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is an elevational view partially in section of a rotary
sprinkler constructed in accordance with the teachings of this
invention with the riser in the lower position.
FIG. 2 is an axial sectional view similar to FIG. 1 with the riser
in the upper position.
FIG. 3 is an axial sectional view through the riser.
FIGS. 3A and FIG. 3B are enlarged, fragmentary, axial sectional
views through the inlet and turbine section taken on a plane
generally perpendicular to the plane of FIG. 3 showing the riser in
the lower and upper positions, respectively.
FIG. 3C is a fragmentary, axial sectional view similar to FIG. 3
with portions removed and taken on a different axial plane.
FIG. 4 is a perspective view with parts removed illustrating the
turbine and portions of the drive train including the shifter and
intermittent motion mechanism.
FIG. 4A is a somewhat schematic view of the gears from the turbine
shaft through the intermittent motion mechanism to the output
shaft.
FIG. 5 is a fragmentary elevational view illustrating a preferred
way for driving the elongated spring element of FIG. 6
overcenter.
FIG. 6 is a front elevational view of a preferred form of
overcenter spring device.
FIG. 6A is a rear elevational view of the overcenter spring device
with the spring element in the same position as in FIG. 6 and
showing some of the supporting structure for the overcenter spring
device.
FIGS. 6B and 6C are simplified views similar to FIG. 6A
illustrating operation of the overcenter spring device.
FIG. 7 is a plan view partially in section illustrating one
embodiment of shifter.
FIG. 8 is a view similar to FIG. 5 illustrating how the elongated
spring element can be forced overcenter in the other direction.
FIG. 9 is a view similar to FIG. 7 illustrating movement of the
shifter to the other position to reverse the direction of the
rotational output.
FIG. 10 is a plan view partially in section illustrating the
overcenter spring device and a preferred form of intermittent
motion mechanism.
FIG. 10A is a view similar to FIG. 10 showing a portion of the
intermittent motion mechanism during a pause in rotation.
FIG. 11 is a perspective view of the intermittent motion
mechanism.
FIGS. 12 and 13 are perspective views of the adapter seal.
FIG. 13A is a fragmentary bottom plan view of the adapter seal.
FIG. 14 is an enlarged fragmentary sectional view illustrating a
portion of FIG. 3 adjacent the adapter seal on a larger scale.
FIG. 14A is a sectional view taken generally along line 14A--14A of
FIG. 14.
FIG. 15 is a sectional view similar to FIG. 14 taken on a plane
perpendicular to the plane on which FIG. 14 is taken.
FIGS. 16 and 17 are fragmentary elevational views partially in
section of the sprinkler head and portions of the sprinkler
immediately below the sprinkler head illustrating how the arc of
travel of the sprinkler head can be adjusted.
FIG. 18 is a sectional view taken generally along line 18--18 of
FIG. 16.
FIG. 19 is a longitudinal sectional view through a preferred form
of nozzle.
FIGS. 20 and 21 are rear and front elevational views, respectively,
of the nozzle.
FIG. 20A is a sectional view taken generally along line 20A--20A of
FIG. 20.
FIG. 22 is a perspective view of a preferred tool for use in
removing the nozzle from the sprinkler head.
FIG. 23 is a fragmentary sectional view showing use of the tool to
remove the nozzle from the sprinkler head.
FIG. 24 is a simplified, fragmentary, exploded, perspective view of
an upper portion of the sprinkler with the sprinkler head rotated
relative to the portions of the sprinkler below the sprinkler
head.
DESCRIPTION OF THE PREFERRED EMBODIMENT
FIGS. 1 and 2 show a rotary sprinkler 11 having a supporting
structure which includes a case 13 and a housing 14 of a riser 15.
The case 13 has an inlet 17 (FIG. 2) for receiving irrigation water
from a conduit 19 to which the case is attached. The riser 15 is
normally held in the lower position of FIG. 1 by a coil spring 21
and can be moved to the upper position or popped-up in response to
water pressure from the conduit 19 acting to lift the riser 15
against the biasing action of the spring 21.
With reference to FIG. 3, the sprinkler 11 generally includes a
unidirectional drive motor in the form of a water driven turbine 23
mounted for rotation within the riser 15, a drive train 25
drivingly coupled to and driven by the turbine 23, an overcenter
spring device 27 and a spray head or sprinkler head 29 including a
nozzle 31 defining an outlet 33 mounted for rotational movement and
adapted to receive irrigation water from the inlet 17 (FIG. 2).
Thus, the turbine 23 drives the drive train 25 to rotate the
sprinkler head 29.
To enable the sprinkler head 29 to be rotated in both the clockwise
and counterclockwise directions, the drive train 25 includes a
shifter or reversing device or reversing mechanism 35 (FIGS. 4, 6,
7 and 9) which is drivingly coupled to the overcenter spring device
27 (FIG. 4, 6, and 10). To cause the sprinkler head 29 to rotate
intermittently or to have pauses in its rotation, the drive train
25 includes an intermittent motion mechanism 37 (FIGS. 3, 4, 10 and
11).
The sprinkler 11 also includes an adapter seal 39 (FIGS. 3, 12 and
13) which performs various sealing and mounting functions.
The Inlet and Turbine Section
The inlet and turbine section may be considered as that portion of
the sprinkler 11 from the turbine 23 (FIGS. 3, 3A, and 3B) down
through the inlet 17 (FIGS. 2, 3A and 3B). The inlet and turbine
section may be generally of conventional construction. In the form
shown in FIGS. 3, 3A and 3B, a tubular filter screen 43 is suitably
affixed to the riser 15 at the lower end of the riser. An annular
resilient seal 45 is mounted on a depending boss 47 of the filter
screen 43 and is received within the inlet 17 when the riser 15 is
in the lower position. Specifically, the seal 45 sealingly engages
a sleeve portion 49 of the case 13 and cooperates with the sleeve
portion to form a valve which prevents water under pressure from
the conduit 19 (FIG. 2) from passing through the inlet 17 into the
riser 15 when the riser is in the lower position of FIG. 3A.
When water under pressure is supplied to the inlet 17, it acts
against the seal 45 to force the riser 15 upwardly against the
biasing action of the spring 21 to the upper position of FIG. 3B.
This allows the water under pressure to pass through the filter
screen to the turbine 23.
The turbine 23 comprises a rotor 53 and a stator 51 suitably
fixedly mounted within the riser 15. The stator has openings 55 and
57 through which water can flow to drive the rotor 53 in a
conventional manner. A conventional spring biased bypass valve 59
opens in response to predetermined pressure differential across the
turbine to limit the pressure drop across the turbine 23 to a
predetermined maximum to maintain a predetermined rotor speed.
The rotor 53 is mounted for rotation on an axially extending
turbine shaft 71 (FIGS. 3, 4 and 4A) which in turn is suitably
rotatably mounted on an inner housing 72 (FIGS. 3, 3C and 4A) which
is suitably mounted within the riser 15 and which forms a portion
of the supporting structure. The inner housing 72 includes a
transverse plate or wall 73, which rests on the upper end of the
stator 51 and mounts the lower end of the shaft 71, and a stepped
wall 75 which forms a bearing for the upper end of the shaft 71.
Consequently, rotation of the rotor 53 rotates the shaft 71 to
provide the output for the turbine 23. The inner housing 72 serves
as an unsealed gear box which water can enter to lubricate the
gears contained within it. The inner housing 72 also provides a
flow path 76 (FIG. 3C) leading from just above the rotor 53 to the
adapter seal 39.
The Drive Train 25 and the Mechanism or Device to Reverse Its
Rotational Output
A pinion 77 (FIGS. 3C, 4 and 4A) is mounted on and rotates with the
shaft 71 and drives a double or speed reducing gear 79 along a
lower and larger gear section 81 (FIG. 4A) of the double gear. The
double gear 79 has a smaller or upper gear section or driving gear
83 (FIGS. 4, 4A and 7). These gears, like many of the other gears
described below, provide a speed reduction function.
The shifter 35 is drivable between the position shown in FIG. 7 in
which it drives a driven gear 85 clockwise and the position shown
in FIG. 9 in which it drives the driven gear 85 counterclockwise.
The driven gear 85 is mounted for rotation on a shaft 86. The shaft
86 is received in a bearing 88 (FIG. 4A) on the transverse plate 73
and the gear 85 can rest on the bearing 88.
In this embodiment, the shifter 35 includes a mounting plate 87
having an opening 89 through which the gear section 83 extends and
two groups of gears both of which are driven by the gear section
83. The first group of gears comprises a single gear 91 rotatably
mounted between the mounting plate 87 and an actuating plate 92
(FIGS. 4, 4A and 6), which also forms a part of the shifter 35. The
second group of gears includes gears 93 and 95, and they are also
rotatably mounted between the mounting plate 87 and the actuating
plate 92. The gears 91, 93 and 95 are rotatably mounted by pins
which also serve to join the mounting plate 87 to the actuating
plate 92 such that the entire shifter, which comprises these two
plates and the three gears form a unitary sub-assembly. The driving
gear 83 drives both groups of gears; however, the arrangement is
such that either the gear 91 or the gear 95 is in driving
engagement with the driven gear 85. Because the gears 91 and 95
counter rotate, with the driving gear 83 rotating counterclockwise
as shown in FIG. 7, the gear 95 drives the driven gear 85
clockwise, and with the shifter in the position of FIG. 9, the gear
91 drives the driven gear 85 counterclockwise.
The double gear 79 is mounted for rotation on a shaft 97 which in
turn is mounted by the transverse wall 73 and a bearing 98 (FIG.
4A) which forms a portion of the inner housing 72. A sleeve 99 on
the actuating plate 92 mounts the shifter 35 for pivotal movement
about the shaft 97 between the positions of FIGS. 7 and 9.
The overcenter spring device 27 is drivingly coupled to the shifter
35 for driving the shifter between the positions of FIG. 7 and 9 to
thereby reverse the direction of the driven gear 85 and the
direction of the rotational output of the drive train. Generally
the overcenter spring device 27 includes an elongated spring
element 101 (FIG. 6 and 6A), an input pivot member 103 and an
output pivot member 105 coupled to opposite end portions of the
spring element and a spring retainer 107 for use in pivotally
mounting the input and output pivot members and for holding the
spring element in a bowed configuration. The spring element 101,
which may be constructed of spring steel, is in the form of a flat,
linear member when unrestrained. The input pivot member 103, which
may be constructed of a suitable rigid polymeric material, includes
an input lever 109 having a shoulder 111 with a sharp pivot edge
113 (FIG. 6). Similarly, the output pivot member 105 includes an
output lever 115 and a shoulder 117 with a pivot edge 119 (FIG.
6A).
The retainer 107 is in the form of an elongated frame which
includes spaced parallel longitudinal members 121 and transversely
extending fulcrum members 123. Each of the fulcrum members 123 has
a shallow V-shaped notch with the apex of the V forming a fulcrum
125. The edges 113 and 119 are received in the V-shaped notches and
engage the fulcrums 125, respectively, such that the pivot members
103 and 105 can pivot about the associated fulcrum. A plate 127
extends between and is attached to the longitudinal members 121
intermediate the fulcrums 125 to make the retainer more rigid. The
retainer 107 is held stationary in the inner housing 72 by walls
128 on the inner housing 72 and by the adapter seal 39.
A driver 129, which in this embodiment is in the form of an
inverted U-shaped member integral with the actuating plate 92, has
a web 131 integrally joining two upstanding legs of the driver. The
web has a recess 133 (FIGS. 6A and 10) which slidably receives an
upper region of the output lever 115 to provide a driving
connection between the output lever and the driver 129. The driver
129 may be considered as part of the shifter 35 or the overcenter
spring device 27.
In the position shown in FIG. 6A, the spring element 101 is bowed
in one direction on one side of a reference line or centerline 134,
i.e. a line extending directly between the fulcrums 125. In this
position, the resilience of the spring holds the edges 113 and 119
against the associated fulcrums 125. As explained more fully below,
a rotatable plate 135 (FIGS. 6 and 6A) is driven by the drive train
25 and in turn pivots the input lever. By pivoting the input lever
109 counterclockwise about the fulcrum 125 as viewed in FIG. 6A,
the input lever moves in a direction which is generally transverse
to the direction of elongation of the spring element 101. This
drives the spring element 101 toward the centerline and causes it
to buckle into the compound curve shown by way of example in the
neutral position of FIG. 6B. Further counterclockwise pivotal
movement of the input lever 109 moves the spring element 101 over
the centerline to reverse the direction in which the spring element
is bowed as shown in FIG. 6C. Thus, the spring element 101 serves
as a buckling column spring. In moving overcenter, the spring
element 101 pivots the output lever 115 about its fulcrum 125 to
the position shown in FIG. 6C. Because the retainer 107 is held
against movement in the inner housing 72, the clockwise pivotal
movement of the output lever 115 (FIGS. 6A-6C) forces the driver
129, the plate 92 and the entire shifter 35 to pivot about the
shaft 97 from the position of FIG. 9 to the position of FIG. 7 to
thereby reverse the direction of rotation of the driven gear
85.
It is apparent that a relatively short input motion imparted to the
input lever 109 is sufficient to buckle the spring element 101 and
move it overcenter. Accordingly, the work required to achieve
reversal is minimized.
The gears 85, 91 and 95 are inherently forced into tighter driving
engagement by virtue of the torque transmitted by these gears, and
this tends to resist disengagement of the gears 85 and 95 and 85
and 91. This in turn requires more force from the spring element
101 in order to achieve the disengagement and ultimate reversal of
the rotational output. However, this invention employs the
intermittent motion mechanism 37 which creates intermittent pauses
in the rotational output of the drive train 25. An advantage of the
intermittent motion mechanism 37 is that during a pause the force
urging the gears 91 and 95 into engagement with the gear 85 by
virtue of their rotation is reduced. Consequently, if during a
pause the spring element 101 is only slightly over center, it can
provide sufficient energy to reverse the direction of rotation
thereby minimizing the energy required for shifting.
It should also be noted that the sprinkler 11 is elongated and that
the elongated spring element 101 extends generally longitudinally
of the sprinkler. This enables the spring element 101 to be
relatively long so it can provide greater force for the reversal
and also facilitates locating of the shifter 35 relatively near the
turbine 23, i.e. low down in the drive train 25, where torque is
less and consequently the force tending to hold the gears 91 and 95
in engagement with the gear 85 is correspondingly less. Because
this latter force is reduced, disengagement of the engaged gears of
the shifter is made easier.
The Intermittent Motion Mechanism 37
The intermittent motion mechanism 37 (FIGS. 4A and 11) generally
comprises a driving gear 139 and a driven gear 141 which are
drivingly engageable to create periodic pauses in the rotation of
the driven gear 141. The intermittent motion mechanism 37 as shown
in FIG. 11 is in the form of a multilated tooth intermittent drive
which is capable of being driven and of transmitting motion in both
the clockwise and counterclockwise directions.
The driving gear 139 is itself suitably driven by the driven gear
85 (FIGS. 4A, 7, 9 and 10). In this embodiment, the driven gear 85
drives the driving gear 139 of the intermittent motion mechanism 37
through speed reducing gears which include a small diameter upper
gear section 143 of the driven gear 85 (FIGS. 4 and 4A) which
drives a larger diameter gear 145 (FIGS. 4, 10 and 11), the latter
being an integral part of the driving gear 139. The driving gear
139 has a single driving gear tooth 147 on an upper level and
circumferentially spaced gear tooth surfaces 149 and 151 on a lower
level. The driving gear tooth 147 is equally spaced
circumferentially between the gear tooth surfaces 149 and 151 and
is axially offset from these surfaces. The driving gear 139 also
has a circumferential surface 153, which is preferably circular,
and which is on the lower level and therefore axially offset from
the driving gear tooth 147. The driving gear tooth 147 is an
involute tooth and the gear tooth surfaces 149 and 151 are involute
gear tooth surfaces. Each of the gear tooth surfaces 149 and 151
forms, in effect, one half of an involute gear tooth.
The driven gear 141 has a first set of involute gear teeth 155 on
an upper level or gear section and a second set of involute gear
teeth 157 on a lower level or gear section with the gear teeth of
the first set being both axially and circumferentially offset from
the gear teeth of the second set. The gear teeth of each of the
first and second sets are spaced circumferentially by an amount
sufficient to accommodate another gear tooth of the same size as
the gear teeth of such set and two tooth spaces. Such another
additional gear tooth and such tooth spaces are of a size to
cooperate with the driving gear tooth 147. As shown in FIG. 11, the
teeth of the first set of gear teeth 155 are centered between an
adjacent pair of teeth of the second set 157. Output from the
intermittent motion mechanism 37 is derived from a small gear
section 159 which is above the set 155 of gear teeth. Both the
driving gear 139 and the driven gear 141 are of integral, one-piece
construction.
The driving gear 139 is mounted for rotation about a shaft 161
which is mounted at its lower end by a bearing 163 (FIG. 4A)
mounted on the transverse plate 73 and at its upper end by a
bearing section 167 suitably formed on the inner housing 72. The
driving gear 139 rests on the top of the bearing 163. The driven
gear 141 is rotatably mounted on the shaft 86, and the upper end of
this shaft is received within a bearing section 171 of the inner
housing 72. The driven gear 141 rests on the gear section 143.
In use, the driving gear 139 is rotated and the driving gear tooth
147 is drivingly engageable with the gear teeth of the first set of
gear teeth 155 and the gear tooth surfaces 149 and 151 are
drivingly engageable with the gear teeth of the second set of gear
teeth 157 to drive the driven gear 141. More specifically and as
shown in FIG. 11, the driving gear tooth 147 engages a gear tooth
155a of the first set 155 to impart an initial increment of
rotation to the driven gear 141. As the driving gear tooth 147
passes out of driving contact with the tooth 155a, the gear tooth
surface 149 engages a gear tooth 157a of the second set 157 to
impart a second increment of angular movement to the driven gear
141. While the driving gear tooth 147 is driving the tooth 155a,
the space between the gear tooth surfaces 149 and 151 accommodates
or receives the gear tooth 157a so that there is no interference
between the driving gear 139 and the driven gear 141. After the
gear tooth surface 149 passes out of driving engagement with the
gear tooth 157a, the circumferential surface 153 comes between and
cooperates with the gear teeth 157a and 157b of the second or lower
set of gear teeth as shown in FIG. 10A to substantially retain the
driven gear 141 against rotation when the driving gear tooth 147
and the gear tooth surfaces 149 and 151 are not in driving
engagement with the gear teeth of the first and second sets 155 and
157 of gear teeth, respectively. It is apparent from the foregoing
that each revolution of the driving gear 139 imparts a small
increment of rotation to the driven gear 141. Solely by way of
example, in the illustrated embodiment there is driving engagement
between the driving gear 139 and the driven gear 141 for only about
51.4.degree., and for the remainder of the cycle of rotation of the
driving gear 139, the driven gear 141 is held against rotation by
the cooperation between the circumferential surface 153 and
confronting teeth of the second set of teeth 157. Thus, there is a
pause created during each revolution of the driving gear 139. Of
course, the driving gear 139 could have additional driving gear
teeth and additional gear tooth surfaces, if desired.
Another feature of the intermittent motion mechanism 37 is that it
can transmit motion in both the clockwise and counterclockwise
directions. Because the driving gear 139 is symmetrical about a
reference line 173 (FIG. 10A), and because both of the sets of gear
teeth 155 and 157 are similarly symmetrical, the driving gear 139
can drive the driven gear 141 in either direction.
The Adapter Seal
An intermediate wall or transverse member 177 (FIGS. 3, 14 and 15)
extends across the riser 15 and is suitably fixed to the riser just
above the upper end of the inner housing 72. The adapter seal 39
engages the transverse member 177 immediately below the transverse
member. The adapter seal 39 is integrally constructed from a
suitable elastomeric material and provides a circular lip seal 179
(FIGS. 12-15) around its circular periphery which forms a seal
between the inner periphery of the riser 15 and the outer periphery
of the transverse member 177.
It is necessary that several members of the sprinkler 11 protrude
through the transverse member 177, and the adapter seal 39 provides
seals in each of these instances. Specifically, an output shaft 181
(FIGS. 3, 4A and 14) extends through the transverse member 177 and
has a lower gear 183 and an upper gear 185. The lower gear 183 is
driven by a pinion 187 (FIG. 4A) integral with a larger gear 189
which is driven by the gear section 159 of the driven gear 141 of
the intermittent motion mechanism 37.
The adapter seal 39 has an opening 192 through which the output
shaft 181 extends and an annular lip seal 191 (FIG. 14) for sealing
around the output shaft. The adapter seal 39 also has annular
bosses 193 and 195 (FIGS. 12-14) which are engagable with the
transverse member 177 and the inner housing 72, respectively.
The drive train 25 also includes a rotatable drive shaft 197 (FIGS.
3, 14 and 15) which extends through the central openings 199 and
201 of the transverse member 177 and the adapter seal 39,
respectively. The drive shaft 197 is rotated by the output shaft
181 as described more fully below. The adapter seal 39 has a
central annular projection 203 with an internal lip seal 205 which
forms a dynamic seal around the rotatable drive shaft 197. Thus,
portions of the drive train 25 are on opposite sides of the
transverse member 177 and the adapter seal 39 provides seals
between the drive train and the transverse member.
A portion of the overcenter spring device 27, namely the input
pivot member 103 extends through aligned openings 207 and 209 in
the transverse member 177 and the adapter seal 39, respectively.
The adapter seal 39 has an integral sealing ridge 211 (FIGS. 13A
and 14) which seals between the input pivot member 103 of the
overcenter spring device 27 and the transverse member 177. In
addition, the adapter seal 39 includes a noncircular, tubular
mounting section 213 (FIGS. 13A and 14) for receiving a region of
the overcenter spring device 27, namely an upper portion of the
retainer 107 to thereby assist in mounting the overcenter spring
device in the inner housing 72. The mounting section 213 is itself
received within a tubular section 214 (FIG. 14) of the inner
housing 72. The mounting section 213 has two pairs of spaced tabs
212 (FIG. 13A) for receiving the upper end portions of the
longitudinal members 121 of the retainer 107.
The transverse member 177 includes a projection 215 (FIG. 15) which
extends through an opening 217 of the adapter seal and is received
in an annular internal mounting wall 219 of the inner housing 72 to
thereby assist in mounting the transverse member on the inner
housing. The adapter seal 39 has a radial seal 221 which sealingly
engages the projection 215 to form a seal to prevent liquid from
migrating through the opening 217.
As shown in FIGS. 14 and 15, the upper face of the adapter seal 39
and the lower face of the transverse member 177 are complementary
in shape so that these two members are in engagement over much of
their confronting surfaces. In addition, the adapter seal 39 has an
annular rib 223, which is radially thickened adjacent the opening
209 and which is received in a complementary groove 225 of the
transverse member 177.
The adapter seal 39 is a one piece integral member which performs
many sealing functions including sealing between the periphery of
the transverse member 177 and the riser 15, sealing around the
output shaft 181 and the drive shaft 197, sealing around the input
member 103 and around the projection 215. In addition, the adapter
seal 39 assists in mounting the retainer 107 of the overcenter
spring device 27.
From a broader perspective, the adapter seal 39 excludes liquid and
particulate contaminants from the components in the riser 15 which
are above the adapter seal and outside of a central passage 231
(FIG. 3C) of the drive shaft 197. The lip seal 205 (FIGS. 3C, 14
and 15) seals along a relatively small circumference to thereby
reduce the friction tending to retard rotation of the drive shaft.
Without the adapter seal 39, it would be necessary to provide a
hydraulic seal higher up in the riser 15 at a larger circumference
and correspondingly greater friction.
The Sprinkler from the Adapter Seal 39 to the Nozzle 31
The gear 185 on the output shaft 181 drives the drive shaft 197 via
the drive ring 198 and a clutch 233 (FIG. 14A). More specifically,
the gear 185 engages internal gear teeth 235 of the drive ring 198
to rotate the drive ring. The clutch 233 comprises external teeth
237 extending completely around the outer periphery of the drive
ring 198, tabs 239 on the drive shaft 197 (only one being shown in
FIG. 14A) separated from adjacent lateral regions of the drive
shaft by slots 241 (FIG. 16) and internal teeth 243 on the tabs 239
which mesh with the external teeth 237 of the drive ring 198. In
this embodiment, there are four of the tabs 239 and they are
equally spaced circumferentially. Each of the tabs 239 is somewhat
resilient so that in the absence of a strong resisting force, the
clutch 233, and more specifically the teeth 237 and 243 transmit
rotary motion from the drive ring 198 to the drive shaft 197.
However, the gears between the turbine 23 and the output shaft 197
provide sufficient resistance to being back driven so that the tabs
239 can flex radially outwardly to permit the teeth 243 to slide
over the teeth 237. As explained more fully below, this is useful
in making the sprinkler vandal resistant.
The drive shaft 197 provides the passage 231 for water to flow
toward the nozzle 31 and its rotary motion drives the nozzle and is
also used to provide energy to drive the overcenter spring device
27 over center in both directions. The motion for this latter
function is transmitted from the drive shaft 197 to the overcenter
spring device 27 by a control ring 245 (FIGS. 3C, 5, 8, 16 and 17),
a finger 247 (FIG. 8) on the drive shaft 197 and the rotatable
plate 135 (FIGS. 3C, 4-6 and 8). As shown in FIGS. 3C, 5 and 8, the
rotatable plate 135 is rotatably mounted on top of the transverse
member 177 and is suitably retained by a retainer 249 (FIG. 3C).
The extent to which the rotatable plate 135 can rotate is limited
as by slots 251 (FIG. 4) through which projections 253 (FIG. 3C) of
the transverse member 177 extend.
To enable the rotation oft he rotatable plate 135 to drive the
overcenter spring device 27 overcenter to accomplish reversal in
the direction of rotation of the sprinkler head 29, the rotatable
plate has a narrow opening 255 through which the input pivot member
103 extends (FIGS. 4 and 6A). Normally, the rotatable plate 135 is
held against rotation by the input pivot member 103 which is in one
of its two bistable positions. However, the rotatable plate 135 has
two flexible, resilient arms 257 and 259 (FIGS. 5 and 8) with
radially offset ends which are engagable with a projection 261
(FIG. 5) on the control ring 245 and the finger 247 (FIG. 8) on the
drive shaft 197, respectively, such that the rotatable plate can be
driven in opposite directions.
By way of example, the rotatable plate 135 may rotate 40 degrees in
each direction, i.e. plus or minus 20 degrees on either side of a
neutral position (FIG. 6B) of the spring 101. This defines the
circumferential zone of operation of the rotatable plate 135 and
the arms 257 and 259.
More specifically, rotation of the drive shaft 197 rotates the
sprinkler head 29 which in turn rotates the control ring 245 as
described more fully below (FIG. 3C). Consequently, sufficient
counterclockwise rotation of the drive shaft 197 and the control
ring 245 causes the projection 261 to contact the arm 257 as shown
in FIG. 5 to initiate rotation of the rotatable plate 135 thereby
driving the input pivot member 103 and moving the overcenter spring
device 27 over center. This overcenter movement of the overcenter
spring device 27 reverses the direction of rotation of the gears
and hence of the drive shaft 197 whereupon the drive shaft rotates
in a clockwise direction. This clockwise rotation continues until
eventually the finger 247 (FIG. 8) is brought into engagement with
the end of the arm 259 of the rotatable plate 135 to thereby drive
the plate in the opposite direction and move the overcenter spring
device 27 overcenter. This causes reversal of the direction of
rotation of the gears and of the drive shaft 197 whereupon the
operation described above is repeated. Because the ends of the arms
257 and 259 as well as the finger 247 and the projection 261 are
radially offset, the finger 247 will not drivingly contact the arm
257 and the projection 261 will not drivingly contact the end of
the arm 259.
The drive shaft 197 also drives the sprinkler head or spray head
29. The spray head 29, which may be considered as part of the riser
15 includes a sprinkler head housing 267 (FIG. 3C) and the housing
267 provides an annular inner wall or socket 269 for receiving an
upper end of the drive shaft 197 to mount the spray head 29 for
rotation with the drive shaft. The upper end of the drive shaft 197
in this embodiment is snap fit into a separate bushing 271 which is
received within and bonded to the socket 269. Consequently rotation
of the drive shaft 197 rotates the spray head 29 so the spray head
29 oscillates or rotates in both directions with the drive shaft
197.
The Spray Head 29 and the Nozzle 31
The sprinkler head housing 267 in this embodiment comprises a body
277 molded from a suitable polymeric material, an inner cap 279
(FIG. 3C) of a rigid polymeric material and an outer cap 280 (FIG.
24) of a suitable elastomeric material closing the upper end of the
body. The outer cap 280 is not shown in FIGS. 3, 3C, 16 and 17. The
spray head 29 includes the nozzle 31 (FIGS. 3, 3C and 19-21) and
the sprinkler head housing 267 which includes nozzle mounting
structure for mounting the nozzle on the sprinkler head housing
267. More specifically, the nozzle mounting structure includes a
circumferential wall 281 defining a bore 283 and a supply passage
285 for conveying water under pressure from the passage 231 through
the drive shaft 197 to the bore 283 and to the nozzle 31. In the
form shown in FIG. 3C, the nozzle mounting structure is an integral
portion of the sprinkler head housing 267. The nozzle 31 is
received in the bore 283 so it can receive water under pressure
from the supply passage 285.
With reference to FIGS. 19-21, the nozzle 31 has an inlet 287, an
outlet 289 and a flow passage 291 extending between the inlet and
the outlet. The outlet 289 has a far stream portion 293 and a near
stream portion 295, and as shown in FIG. 21, the outlet is
unpartitioned, i.e. has no partitions, between the far stream and
near stream portions so that a single stream can be emitted from
the outlet. The far stream portion 293 has a center 297, and in
this embodiment, the far stream portion of the outlet is generally
circular about the center 297. The near stream portion 295 of the
outlet 289 is generally rectangular and of smaller cross section
than the far stream portion 293 and together with the far stream
portion 293 forms a somewhat keyhole-shaped outlet.
The flow passage 291 also has a far stream portion 299 and a near
stream portion 301 leading to the far stream portion 293 and near
stream portion 295, respectively of the outlet 289. The flow
passage 291 is also unpartitioned between its far stream portion
299 and its near stream portion 301.
The far stream portion 299 and the near stream portion 301 of the
flow passage 291 are configured to provide higher velocity less
turbulent flow through the far stream portion 293 of the outlet 289
than through the near stream portion 295 of the outlet 289.
Consequently, the stream emitted from the far stream portion 293
retains a more rod-like configuration and travels farther than the
water emitted from the near stream portion 295.
Although this result may be obtained in different ways, in the
illustrated embodiment, the far stream portion 299 of the flow
passage 291 converges toward the center 297 of the far stream
portion 293 of the outlet 289 as it extends toward the outlet and
the near stream portion 301 of the flow passage is less convergent
toward the center 297 of the far stream portion 299 of the outlet
as it extends toward the outlet than the far stream portion 299 of
the flow passage. Consequently, the far stream portion 299 of the
flow passage 291 provides a portion of the stream which can travel
farther than the portion of the stream which is provided by the
near stream portion 301 of the flow passage.
More specifically, the far stream portion 299 of the flow passage
291 has a smooth curved surface 303 which is part annular and which
extends almost completely around the far stream portion 299 of the
flow passage. The nozzle 31 includes radially extending vanes 305
(four being shown in FIG. 20) on the curved surface 303 for
directing water toward the far stream portion 293 of the outlet
289. In this embodiment, the vanes 305 extend axially and radially
and are circumferentially spaced. The curved surface 303 converges
toward the far stream portion 293 of the outlet 289 such that the
far stream portion 293 forms, in effect, the throat of a nozzle.
Consequently, the water flowing toward the far stream portion 293
of the outlet 289 is crowded together to increase the velocity head
of the stream with reduced turbulence to provide a stream portion
which will travel relatively far.
The near stream portion 301 of the flow passage 291 has a
longitudinal, generally trough-shaped surface 307 which extends
toward the near stream portion 295 of the outlet 289 and which is
essentially non-inclined radially inwardly as it extends toward
such near stream portion of the outlet. The trough-shaped surface
307 includes substantially flat surfaces 309 which meet at an apex
to form a shallow V or shallow trough. The flat surfaces 309 extend
longitudinally toward the near stream portion 295 of the outlet
289. It can be seen therefore that the near stream portion 301 of
the flow passage 291 is less convergent toward the center 297 of
the far stream portion 293 of the outlet 289 as it extends toward
the outlet than the far stream portion 299 of the flow passage.
The near stream portion 301 of the flow passage 291 preferably has
one or more ledges 311 adjacent the outlet 289 which narrows the
near stream portion 301 of the flow passage and provides water for
intermediate distances. In this embodiment, there are two of such
ledges 311 on opposite sides of the near stream portion 301 of the
flow passage 291. The ledges 311 narrow the near stream portion 301
of the flow passage 291 and assist in providing some water for
intermediate distances.
The nozzle 31 has an inlet section 313 of larger cross sectional
area than the combined cross sectional areas of the far stream
portion 299 and the near stream portion 301 of the flow passage
291. The inlet section 313 is upstream of the far stream portion
299 and the near stream portion 301 of the flow passage 291. The
flow passage 291 has a turbulence creating surface between the
inlet section 313 and the near stream portion 301 of the flow
passage 291 for causing turbulence in the water flowing from the
inlet section to the near stream portion 301 of the flow passage.
Preferably, the turbulence creating surface includes a ledge 315
facing the inlet 287.
The nozzle 31 has a peripheral wall 317 which includes a main body
319 and a hood 321 which is radially offset from the main body to
form opening 323. In this embodiment, the main body 319 is
generally cylindrical about the center 297 and the hood 321
includes a generally cylindrical section having a center 325 which
is radially offset from the center 297 as shown in FIG. 21. The
hood provides an abutment 327 for engagement by a tool 329 (FIGS.
22 and 23) as described more fully below for withdrawing the nozzle
31 from the bore 283. The opening 323 allows the tool 329 to gain
access to the abutment 327 for this purpose.
The nozzle 31 includes vanes 331 (three being shown in FIG. 21)
between the hood 321 and the main body 319 for strengthening
purposes and for directing water from the opening 323 as described
more fully hereinbelow. The central vane 331 includes a rib 333
which extends between the main body 319 and the hood 321 and across
the opening 323 to bifurcate the opening.
The nozzle 31 is received in the bore 283 as shown in FIGS. 3 and
3A. To retain the nozzle 31 in the bore 283, a threaded fastener in
the form of a screw 335 extends through an upper region of the
sprinkler head housing 267 and through a groove 337 (FIGS. 3C, 19
and 21) of the hood 321. Thus, the main body 319 and the hood 321
are received in the bore 283 so that the nozzle 31 can receive
water under pressure from the supply passage 285 so water can pass
through the flow passage 291 and outlet 289 to form a stream. The
pressure of the water from the supply passage 285 acting on the
nozzle 31 tends to pivot or tilt the nozzle in the bore 283 about
an axis which is generally transverse to the flow passage 291. More
specifically, the screw 335 forms a fulcrum about which the nozzle
31 tends to pivot. The nozzle 31 tends to pivot clockwise as viewed
in the FIG. 3C about the fulcrum formed by the screw 335. This
tendency to pivot tends to separate regions of the peripheral wall
317 and the circumferential wall 281 to form a leakage path 339
(FIGS. 3 and 3C) which leads to the opening 323. The leakage path
directs any such leakage toward the stream emanating from the
outlet 289 downstream of the outlet 289. Thus, any such leakage can
form a part of the stream emitted from the outlet 289.
It should be understood that the so-called leakage path 339 may or
may not exist depending on various factors such as temperature,
tolerances, warping of the nozzle or the bore 283, etc. and is
greatly exaggerated in FIG. 3C. Thus the leakage path may be a
tight interface through which no water passes. However, this
feature of the invention recognizes that in some circumstances
there will be some leakage passing through the path 339 and
provides for return of this water to the flow stream from the
outlet such that the leakage is not uncontrolled.
It should also be noted that the radial offset of the hood 321 and
the peripheral wall 317 provides an advantageous way to create the
opening 323 for the leakage path 339. Also, the vanes 331 tend to
direct any leakage from the opening 323 to the stream from the
outlet 289.
With this construction, the sprinkler head 267 and the nozzle 31
are driven back and forth through an arc of predetermined length.
During this time, water flows from the passage 231 (FIG. 3C)
through the supply passage 285, the flow passage 291 of the nozzle
31 and the outlet 289 of the nozzle. The water flowing through the
far stream portion 299 of the flow passage 291 is caused to
converge by the curved surface 303 and to accelerate through the
far stream portion 293 of the outlet 289 to form the far stream
portion of the stream, i.e. the portion of the stream that will
travel a relatively great distance from the sprinkler 11. On the
other hand, water striking the ledge 315 is made relatively
turbulent and the water passing through the near stream portion 301
of the flow passage 291 is restricted or converged much less than
the water flowing through the far stream portion 299. Consequently
the water forming the near stream portion has reduced velocity
energy and this causes this portion of the stream to fall off more
quickly to water regions nearer to the sprinkler 11. Any leakage
through the path 283 passes through the opening 323 and rejoins the
stream emanating from the outlet 289.
Another feature of the invention is that the nozzle 31 can be
easily removed from the sprinkler head housing 267 utilizing the
tool 329 without damage to the critical nozzle surfaces. As shown
in FIG. 22, the tool 329 comprises a body 341 having three finger
rings 343 and three elongated arms 345, 347 and 349 projecting from
the body 341. The central arm 347 has two tabs 351 separated by a
gap 353.
To remove the nozzle 31 from the sprinkler head housing 267, the
screw 335 is removed sufficiently so that it does not impede
withdrawal of the nozzle 31 from the bore 283. The leg 347 is
inserted into the hood 321 as shown in FIG. 23 with the tabs 351
being received in the opening 323 on opposite sides of the rib 333
of the central vane 331 such that the tabs engage the abutment 327.
The nozzle 31 can then be removed by an outwardly directed force as
shown in FIG. 23. The arms 345 and 349 are not needed for nozzle
withdrawal feature, but can be provided for other purposes, if
desired.
The Arc Setting
To establish a zero point for adjusting the arc through which the
sprinkler head 29 moves, the sprinkler 11 has a marker 359 (FIG.
24) on the exterior of the riser 15 which is axially aligned with
the confronting ends of the arms 257 and 259 (FIGS. 4, 5, 8 and 24)
of the rotatable plate 135. Arc adjustment is accomplished by
rotating the control ring 245 (FIGS. 5, 8, 16, 17 and 24) with
respect to the finger 247 (FIGS. 8 and 24) and the ends of the arms
257 and 259 or with respect to the marker 359 which marks the
location of the ends of these arms.
The sprinkler 11 has an arc controller for controlling the
magnitude of the arc through which the sprinkler head can rotate.
The arc controller includes the finger 247 (FIGS. 8 and 24), the
projection 261 (FIGS. 5 and 24) and the arms 257 and 259 (FIGS. 5,
8 and 24). The sprinkler 11 also includes an arc adjuster for
adjusting the arc controller to thereby adjust the arc through
which the sprinkler head 29 can rotate. This adjustment to the arc
controller adjusts the circumferential spacing between the finger
247 and the projection 261.
The arc adjuster includes an arc adjust driver in the form of an
arc adjust stem of arc adjusting stem 361 (FIGS. 3, 3C, 16, 17 and
24), an arc adjust member 362 and the control ring 245 (FIGS. 5, 8,
16, 17 and 24) which carries the projection 261. The arc adjusting
stem 361 (FIG. 16 and 17) is rotatably mounted in the sprinkler
head housing 267 and is biased upwardly by a coil compression
spring 363. The arc adjusting stem 361 has a head 365 at its upper
end with a socket 366 (FIG. 3C) to receive an appropriate tool and
a pinion 367 at its lower end. Locking splines 368 (FIG. 16) on the
stem 361 and the outer cap 280 allow the stem 361 to be moved
axially between an upper position of FIG. 16 and a lower position
of FIG. 17. The splines 368 hold the stem against rotational
movement when the stem is in its upper position (FIG. 16) and allow
the stem 361 to be rotated in the lower position (FIG. 17).
The pinion 367 meshes with a gear section or arc adjusting gear 369
of the arc adjust member 362. The arc adjust member 362 is mounted
for rotational movement with the sprinkler head 29 as described
more fully below. The arc adjust member 362 has a series of
radially inwardly extending internal teeth or projections 371
(FIGS. 18 and 24) which mesh with mating teeth 373 on an upwardly
extending stem 375 (FIGS. 16, 18 and 24) of the control ring 245
thereby drivingly coupling the arc adjust member 362 to the
projection 261 and enabling rotation of the arc adjust member 362
relative to the sprinkler head 29. Consequently, rotation of the
pinion 367 rotates the control ring 245 and the projection 261 on
the control ring to thereby change the circumferential spacing
between the projection 261 and the arm 257 and between the
projection 261 and the finger 247. This circumferential spacing
defines the arc through which the sprinkler head 29 will
rotate.
In operation, rotation of the drive shaft 197 rotates the sprinkler
head 29 through the bushing 271 and the socket 269 (FIG. 3C). As
the sprinkler head 29 rotates in one direction, it either advances
the projection 261 toward the associated arm 257 or the finger 247
toward the associated arm 259. More specifically rotation of the
sprinkler head 29 with the pinion 367 of the arc adjusting stem 361
meshing with the arc adjusting gear 369 causes rotation of the arc
adjusting gear 369 with the sprinkler head 29 and consequent
rotation of the control ring 245 by virtue of the engagement of the
teeth 371 and 373 (FIG. 18). Consequently, the control ring 245 and
its projection 261 rotate with the sprinkler head 29. Because the
finger 247 is on the drive shaft 197, it also rotates with the
drive shaft and with the sprinkler head. Because both the
projection 261 and the finger 247 move with the sprinkler head 229,
they can be used to reverse the direction of movement of the
sprinkler head and to establish the arc through which the sprinkler
head 29 rotates.
Assuming, for example, that the direction of rotation of the
sprinkler head 29 is such as to move the projection 261 toward the
arm 257, eventually the projection will contact the arm as shown in
FIG. 5 and thereby rotate the rotatable plate 135 to move the input
pivot member 103 to move the overcenter spring device 27 overcenter
as described above in connection with FIGS. 6A-6C. This brings
about reversal of the direction of rotation of the drive shaft 197
as also described above whereupon the sprinkler head 29 reverses
its direction of rotation to move the finger 247 toward the arm
259. When the finger 247 contacts the arm 259 as shown in FIG. 8,
it counter rotates the rotatable plate 135 to move the overcenter
device 27 overcenter in the opposite direction to again reverse the
direction of rotation.
The arc adjusting member 362 has a wall or annular flange 377 (FIG.
3C, 16, 17 and 24) with a projection forming a pointer 379 which is
visible from outside the sprinkler 11 between the sprinkler head
housing 267 and the portions of the housing 14 of the riser 15. As
best seen in FIGS. 17 and 24, the pointer 379 is in axial alignment
with the projection 261 such that the pointer can indicate the
circumferential location of the projection 261. Also, the marker
359 (FIG. 24) is in axial alignment with the confronting ends of
the arms 257 and 259 (FIGS. 4, 5, 8 and 24). Consequently, the
locations of the projection 261 and the confronting ends of the
arms 257 and 259 are known from the exterior of the sprinkler 11,
and the marker 359 and pointer 379 visually indicate the locations
of the opposite ends of the arc through which the sprinkler head 29
can rotate.
Preferably, the sprinkler head 29 is supplied by the manufacturer
with the nozzle 31 in approximately axial alignment with the marker
359. To install the sprinkler 11 with the desired arc of rotation,
the sprinkler is positioned with the marker 359 aimed at the right
edge of the arc, e.g. at 3 o'clock. Using an appropriate tool, such
as the arm 345 of the tool 329, the arc adjusting stem 361 is
depressed to the position of FIG. 17 to unlock the locking splines
368 and then rotated to rotate the arc adjust member 362, the
pointer 379 of the arc adjust member and the projection 261
relative to the sprinkler head 29 to a desired location to
establish the other edge of the arc. The angular magnitude of the
arc can be ascertained by the pointer 379 and indicia 381 (FIG. 24)
on the outer cap 280 of the sprinkler head 29. Specifically the
magnitude of the arc is indicated by the number of the indicia 381
which is in axial alignment with the pointer 379. In this manner,
the arc of rotation is determined and oriented with respect to the
surface to be irrigated. The arc of watering can be adjusted from a
very small arc roughly equal to the arc size required for reversing
rotation of the sprinkler head 29 to 360.degree. or more. The
finger 247 is circumferentially offset from the nozzle 31 an amount
which defines the minimum arc of rotation of the sprinkler head
29.
The sprinkler 11 also has a vandal resistant feature in that any
turning of the sprinkler head 29 beyond the preset arc results in
slippage of the clutch 233 (FIG. 14A) to thereby protect the gear
train against damage. The arms 257 and 259 (FIG. 4) are
sufficiently flexible in the axial and radial directions to permit
them to be forcibly biased by the projection 261 and the finger 247
so that the projection and finger can ride over these arms if a
sufficient force, which greatly exceeds normal operating forces, is
applied. Manual rotation of the sprinkler head 29, such as by a
vandal, may also direct the nozzle 31 outside of the desired
watering arc. In addition the arms 257 and 259 do not move outside
their circumferential zone of operation, e.g. plus or minus
20.degree., and so the sprinkler will self-correct and
automatically return to the desired watering arc thereby providing
a memory arc feature.
The arc adjust member 362 also provides a plurality of seals which
exclude grit from a bearing 382 (FIG. 3C) which circumscribes the
drive shaft 197 adjacent the sprinkler head 29 and which forms a
portion of the supporting structure for the sprinkler 11. For
example, the flange 377 terminates radially outwardly in a static
seal 383 (FIGS. 3C, 16 and 17) which is integral with the arc
adjust member and which sealingly engages an inner annular surface
385 of the sprinkler head housing 267. In addition, the gear
section 369 includes an annular wall 387 (FIG. 18) having external
gear teeth 389 (FIG. 18) and an internal surface 391 (FIGS. 3C and
18) sealingly receiving the upper end of the inner wall or socket
269 of the housing 267 of the sprinkler head 29 to thereby provide
a second static seal integral with the arc adjust member 362. The
internal wall 391 receives the inner wall 269 so as to allow these
walls to slide relative to each other for arc adjustment but snugly
enough to serve as a grit seal.
The arc adjust member 362 also includes an annular dynamic seal 393
(FIG. 3C) depending from the wall or flange 377 and sealingly
engaging the bearing 382. The seal 393 rotates with the sprinkler
head and the bearing 382 is stationary and so the seal 393 is a
dynamic seal.
The arc adjust member 362 is preferably a one-piece member and can
advantageously be integrally molded of a polymeric material. At
least radial outer portions of the flange 377 are preferably
resiliently flexible so that the seal 383 is resiliently biased
against the inner surface 385. The seals 383 and 393 and the static
seal provided by the internal surface 391 exclude grit from the
three possible grit paths which lead to the bearing 382.
Although an exemplary embodiment of the invention has been shown
and described, many changes, modifications and substitutions may be
made by one having ordinary skill in the art without necessarily
departing from the spirit and scope of this invention.
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